Linear rolling bearing for the transmission of torques

ABSTRACT

A linear rolling bearing for transmitting torques about its longitudinal axis, having an inner profile element ( 2 ) and an outer profile element ( 1 ) which surrounds the inner profile element ( 2 ) at least partially, the two profile elements ( 1, 2 ) being mounted via rolling bodies ( 3 ) such that they can be displaced with respect to one another in the longitudinal direction, which rolling bodies ( 3 ) circulate endlessly in at least one first circulatory channel ( 5 ) and in at least one second circulatory channel ( 6 ), the circulatory channel ( 5, 6 ) having a loadbearing channel ( 7, 10 ) which is parallel to the longitudinal axis, a return channel ( 8, 11 ) which is parallel to the longitudinal axis, and two deflection channels ( 9, 12 ) which connect the loadbearing channel ( 7, 10 ) and the return channel ( 8, 11 ) to one another in an endless manner, the rolling bodies ( 3 ) which are arranged in the loadbearing channel ( 7 ) of the first circulatory channel ( 5 ) being provided for transmitting a torque between the two profile elements ( 1, 2 ), and the rolling bodies ( 3 ) which are arranged in the loadbearing channel ( 10 ) of the second circulatory channel ( 6 ) being provided to transmit a torque in the opposite direction between the two profile elements ( 1, 2 ), it being possible to connect the first circulatory channel ( 5 ) and the second circulatory channel ( 6 ) to one another for jointly transmitting torques, the return channel ( 8, 11 ) of the circulatory channel ( 5, 6 ) which can be respectively connected being used as a loadbearing channel and the loadbearing channel ( 7, 10 ) of the circulatory channel ( 5, 6 ) which can be respectively connected being used as a return channel.

The present invention relates to a linear rolling bearing fortransmitting torques. Linear rolling bearings of this type are used invirtually all areas of mechanical engineering and motor vehicletechnology. Parts which can be displaced longitudinally with respect toone another can be mounted with bearings of this type. In applicationswith shafts whose lengths can be adjusted telescopically, a bearing ofthis type has to additionally transmit the torques which are passedthrough the shaft. Shafts whose length can be adjusted telescopicallyare used, for example, as steering shafts of steering columns of modernmotor vehicles. In steering columns of this type, the position of thesteering wheel in the passenger compartment can be adapted to theindividual size and posture of the operating person. In this way, theabsolute spacing of the steering wheel with respect to the steering gearis changed. This change in spacing can be corrected by two shaft endswhich are arranged inside one another so as to be displaceabletelescopically.

For example, DE 199 33 875 A1 has disclosed a linear rolling bearing asclaimed in the features of the precharacterizing clause of claim 1. Thetwo profile elements can be displaced satisfactorily in the longitudinaldirection with respect to one another. This is achieved by the rollingmounting, the rolling bodies circulating in endless circulatorychannels. Torques of small magnitude can be transmitted between the twoprofile elements via the rolling bodies. However, if the prevailingtorque exceeds a critical value, the two profile elements rotate atleast by a small rotational angle with respect to one another underresilient work, wall sections of both profile elements coming intocontact with one another. The magnitude of the torque which is stilltransmitted via the rolling bodies can be defined by the design of thecompressing elements. Above a critical torque, at any rate, thetransmission takes place via the abovementioned contacts of the wallsections of the two profile elements with one another. In this knownlinear rolling bearing, the rolling bodies circulate in first and insecond circulatory channels. Both circulatory channels have aloadbearing channel which is parallel to the longitudinal axis, torquesor radial loads below the critical torque being transmitted between thetwo profile elements via the rolling bodies which are arranged in theloadbearing channel. Furthermore, said circulatory channels have areturn channel which is parallel to the longitudinal axis and in whichthe rolling bodies return without load. The return channel and theloadbearing channel are connected to one another in an endless mannervia deflection channels, with the result that the rolling bodies cancirculate endlessly. The rolling bodies which are arranged in theloadbearing channel of the first circulatory channel can transmittorques in one rotational direction. The rolling bodies which arearranged in the loadbearing channel of the second circulatory channelcan transmit torques in the opposite direction between the two profileelements.

Although the contact of the wall sections of the two profile elementswith one another ensures that the rolling bodies of the two circulatorychannels are not exposed to any excessively high loadings as a result ofovercritical torques, it is to be noted that a simultaneous relativedisplacement of the two profile elements with respect to one another inthe longitudinal direction is possible above the critical torque onlywith friction work. This is because sliding friction is caused duringthe contact of the wall sections, a frictional force being a function ofthe prevailing torque.

It is therefore an object of the present invention to specify a linearrolling bearing as claimed in the features of the precharacterizingclause of claim 1, in which a relative displacement of the two profileelements in the longitudinal direction is also possible without problemsunder torque loading.

According to the invention, this object is achieved by the fact that thefirst circulatory channel and the second circulatory channel can beconnected to one another for jointly transmitting torques, the returnchannel of the circulatory channel which can be respectively connectedbeing used as a loadbearing channel and the loadbearing channel of thecirculatory channel which can be respectively connected being used as areturn channel.

In the linear rolling bearing according to the invention, the slidingcontact of the profile elements is absent at torques above a criticaltorque. Even torques above the critical torque are transmittedexclusively via the rolling bodies between the two profile elements. Thecontrivance of the invention is to be seen in the fact that, in bothrotational directions above the critical torque, the forces which occurare transmitted not only by the rolling bodies of the first or thesecond circulatory channel, but by the rolling bodies of the twocirculatory channels. In other words, the invention can be described bythe fact that, below a critical torque, substantially only theloadbearing channel of the first or of the second circulatory channel isprovided for transmitting the torque, the return channel of therespective other circulatory channel being provided additionally abovethe critical torque as a loadbearing channel for transmitting thistorque, and the loadbearing channel of said other circulatory channelbeing provided as a return channel. Therefore, only a reversal of theloadbearing channel and the return channel takes place in the connectedcirculatory channel.

The first or second circulatory channel can be connected to therespective other circulatory channel in different ways. In one variantwhich is preferred in accordance with the invention, a rotational angle(even if it is small) of the two profile elements with respect to oneanother about the longitudinal axis is a function of the prevailingtorque, a critical rotational angle being exceeded above the criticaltorque, at which critical rotational angle the return channel is used asa loadbearing channel and the loadbearing channel is used as a returnchannel in the circulatory channel which is connected. Accordingly,below this rotational angle, the conditions in the loadbearing channeland in the return channel of the connected circulatory channel change,as will be explained in the following text.

In a known way, the loadbearing channel and the return channel aredelimited in each case by an outer raceway for the rolling bodies, whichouter raceway is assigned to the outer profile element, and by an innerraceway for the rolling bodies, which inner raceway is assigned to theinner profile element. The same is also true for the deflection channelsof the two profile elements which are delimited in each case by an outerdeflection track which is assigned to the outer profile element and byan inner deflection track which is assigned to the inner profileelement.

Likewise in a known manner, the rolling bodies are arranged without playin the loadbearing channel, in roller contact with the raceways whichdelimit the loadbearing channel. It is ensured in this way that there isno rotational play between the two profile elements. Furthermore, therolling bodies are arranged in the return channel with play with respectto the raceways which delimit the return channel. This is necessary, inorder that the balls can be returned as far as possible withoutfriction, in order to be deflected into the loadbearing channel again.

According to the invention, the play of the rolling bodies in the returnchannel of the circulatory channel which can be connected is reducedduring the rotation (even if it is small) of the two profile elementswith respect to one another. Furthermore, the play of the rollingbodies, with respect to the raceways, in the loadbearing channel of thecirculatory channel which can be connected is increased during therotation. This influencing of the play of the rolling bodies in thereturn channel and in the loadbearing channel is possible inarrangements with a first and with a second circulatory channel, thefirst circulatory channel being provided for transmitting torques in onerotational direction, and the other circulatory channel being providedfor transmitting torques in the opposite rotational direction.

In a linear rolling bearing according to the invention which ispreferred from a technical and economic viewpoint, the outer profileelement can have a hollow body and the inner profile element can have ashaft, a plurality of segments which are distributed over thecircumference and delimit the circulatory channels together with theshaft being provided between the hollow body and the shaft. Everysegment can be provided with the two raceways which are arrangedparallel to one another, and with two deflection tracks which connectsaid raceways to one another. Segments of this type can be manufactured,for example, as a punched part cheaply. As a result of the provision ofa plurality of segments, even small relative movements of the segmentsin the circumferential direction with respect to one another can be madepossible, in order to avoid stressing between the two profile elementswithin the permissible tolerances.

The hollow body can be, for example, a tube, or else a sleeve or a ring.

Every segment can be supported on the hollow body in order to transmit atorque. For this purpose, the outer raceway can be configured as a ballgroove on that side of the segment which faces the shaft, a convexshaped-out molding of the segment being formed on its side which facesthe hollow body. Said convex shaped-out molding of the segment can bearagainst a rest of the hollow body in order to transmit a torque. If thesegment is manufactured from a metal plate with an identical wallthickness, that side of the metal sheet which faces the shaft can beprovided with the ball groove which corresponds to a concave recess, theabovementioned convex shaped-out molding being produced by this pressingin of the recess on that side of the segment which faces thehollow-cylindrical body.

The hollow body can be provided with a plurality of shaped recesseswhich are distributed over the circumference, project radially inwardlyand form the rests for the segments in order to transmit a torque.

The shaft is preferably provided with a plurality of teeth which aredistributed over the circumference, are arranged parallel to thelongitudinal axis and on which the raceways are formed. The raceways arepreferably formed as ball grooves.

Teeth which are adjacent to one another delimit in each case a convexlycurved circumferential section between them. This circumferentialsection which is as a rule partially cylindrical can delimit thedeflection channel as a deflection track for the rolling bodies.

According to the invention, the hollow body can be deformed resilientlyin a particularly advantageous manner. This property makes it possiblein a simple manner to rotate the two profile elements with respect toone another, a resilient deformation of the hollow body being associatedwith this rotation. If the torque is removed again, the hollow body isdeformed back again, with the result that the initial position isreached again.

Another possible way of implementing the invention can provide, forexample, spring elements which are arranged between the segments and thehollow body, the segments being supported in the circumferentialdirection by the hollow body via the spring elements.

In the following text, the invention will be explained in greater detailusing an exemplary embodiment which is illustrated in a total of twofigures, in which:

FIG. 1 shows a cross section through a linear rolling bearing accordingto the invention, and

FIG. 2 shows the linear rolling bearing according to the invention fromFIG. 1, in an exploded illustration in perspective.

The linear rolling bearing according to the invention which isillustrated in FIGS. 1 and 2 has an outer profile element 1 and an innerprofile element 2. Rolling bodies 3 which are preferably configured asballs 4 are arranged between the two profile elements 1, 2. The balls 4circulate endlessly in two first circulatory channels 5 and in twosecond circulatory channels 6, the two first circulatory channels 5 andthe two second circulatory channels 6 lying diametrically opposite oneanother. The first circulatory channel 5 comprises a loadbearing channel7 which is arranged parallel to the longitudinal axis of the linearrolling bearing, a return channel 8 which is likewise arranged parallelto the longitudinal axis of the linear rolling bearing, and twodeflection channels 9 which connect the loadbearing channel 7 to thereturn channel 8 in an endless manner and which can be seen clearly inFIG. 2.

The second circulatory channel 6 comprises a loadbearing channel 10which is arranged parallel to the longitudinal axis, a return channel 11which is arranged parallel to the longitudinal axis, and two deflectionchannels 12 which connect the loadbearing channel 10 and the returnchannel 11 to one another in an endless manner.

The outer profile element 1 is composed of a hollow body 13 which isconfigured as a tube 14 in the present case, and further of foursegments 15, 16 which are distributed over the circumference, twosegments 15 being assigned to the first circulatory channel 5 and twosegments 16 being assigned to the second circulatory channel 6. It canbe gathered clearly from FIG. 2 that the segments 15, 16 are eachprovided with an endless ball track for the balls 4. On their sideswhich face the inner profile element 2, the segments 15 are providedwith raceways 17, 18 which are configured as ball grooves 19, 20 in thepresent case. The ball grooves 19 delimit the return channel 8, and theball grooves 20 delimit the loadbearing channel 7. In a correspondingmanner, the segments 16 are provided, on their sides which face theinner profile element 2, with raceways 21, 22 which are configured asball grooves 23, 24 in the present case. The ball grooves 23 delimit thereturn channel 11 of the second circulatory channel 6, and the ballgrooves 24 delimit the loadbearing channel 7 of the second circulatorychannel 6.

In each case one cap 25 which is provided as a captive securing meansfor the balls 4 is arranged between the loadbearing channel 7 and thereturn channel 8 of every circulatory channel 5, 6. If the outer profileelement 1 is pulled off from the inner profile element 2, the balls 4cannot fall out inwardly from the outer profile element 1, as the caps25 catch the balls 4 underneath. In normal operation of the linearrolling bearing according to the invention, the caps 25 are notnecessarily required, and could also be removed.

Every segment 15, 16 has an annularly closed endless pressed-in portion,as can be seen in the perspective illustration of FIG. 2 on the outerside of the segments 15, 16. Said pressed-in portions form theabove-described ball grooves 19, 20, 23, 24 on the sides which face theinner profile element 2. The segments 15, 16 have approximately the samewall thickness over their entire extent. Accordingly, convex shaped-outmoldings 26, 27 correspond to the pressed-in portions on the inner sideof the segments 15, 16, the shaped-out moldings 26 being formed on thesegments 15 and, from them, the shaped-out moldings 27 being formed onthe segments 16.

The tube 14 is provided with a plurality of shaped recesses 28 which aredistributed over the circumference and project radially inwardly, ineach case one of said shaped recesses 28 being arranged between twoshaped-out moldings 26, 27 of two segments 15, 16 which are arrangednext to one another. It can be seen clearly from FIG. 1 that theshaped-out moldings 26, 27 are supported on the shaped recesses 28 inthe circumferential direction.

It can be seen clearly from FIG. 2 that deflection tracks 29 are formedon the segments 15, as a result of the abovementioned pressed-inportions, and deflection tracks 30 are formed on the segments 16 for theballs 4, the deflection tracks 29, 30 connecting the ball grooves 19,20, 23, 24 of the respective segments 15, 16 to one another in anendless manner.

In the present case, the inner profile element 2 is formed by a shaft31. Said shaft 31 has four teeth 32 which are distributed over thecircumference and project radially outward out of the cylindrical faceof the shaft 31, every tooth 32 being arranged parallel to thelongitudinal axis and being formed along the shaft 31. In each case onetooth 32 engages between two first and second circulatory channels 5, 6which are arranged next to one another. It can be seen clearly from FIG.1 that, starting from the top and rotating in the clockwise direction,the first tooth 32 engages between two return channels 8, 11 of thefirst and the second circulatory channel 5, 6, that the next tooth 32engages between two loadbearing channels 7, 10 of the first and thesecond circulatory channel 5, 6, that the next (i.e. lowermost) tooth 32engages between two return channels 8, 11, and that the last tooth 32engages between two loadbearing channels 7, 10 again.

In each case one ball groove 33, 34 is formed on both longitudinal sidesof every tooth 32, the ball groove 33 being assigned to the secondcirculatory channel 6 and the ball groove 34 being assigned to the firstcirculatory channel 5. The ball grooves 33, 34 delimit in each case thereturn channels 8, 11 or the loadbearing channels 7, 10.

Two teeth 32 which are arranged next to one another delimit in each caseone cylindrical circumferential section 35 of the shaft 31. Saidcylindrical circumferential section 35 delimits the deflection channel9, 12. The balls 4 roll along said cylindrical circumferential section35, in order to pass from the return channel 8, 11 into the loadbearingchannel 7, 10.

The balls 4 are arranged without play in the loadbearing channels 7, 10.This means that there is no play in the rotational directions betweenthe outer profile element 1 and the inner profile element 2.

The tube 14 of the outer profile element 1 is configured and dimensionedin such a way that it can be deformed under the action of a prevailingtorque.

In the following text, the method of operation of the linear rollingbearing according to the invention will be explained in greater detailusing FIG. 1. Initially, it is to be assumed that there is no torque,that is to say no torque is being transmitted between the two profileelements 1, 2. The outer profile element 1 is displaced longitudinallywith respect to the inner profile element 2 as the balls 4 roll on theball grooves 20, 24, 33, 34 of the loadbearing channels 7, 10. It can beseen from FIG. 1 that the play S is formed in the return channels 8, 11,that is to say the balls 4 can return satisfactorily. If then, forexample, a torque is introduced into the shaft 31 in the clockwisedirection, this torque is transmitted by the balls 4 which are arrangedin the loadbearing channels 7 of the first circulatory channels 5. Inthe illustration according to FIG. 1, these are the balls 4 of the firstand third quadrants. If a torque is introduced into the shaft 31 in thecounterclockwise direction, this torque is transmitted by the balls 4which are arranged in the loadbearing channels 10 of the secondcirculatory channels 6. In the illustration according to FIG. 1, theseare the balls 4 of the second and fourth quadrants. As long as themagnitude of the torques remains considerably below a critical value,the situation remains largely as shown in FIG. 1. This means that theplay S is formed in the return channels 8, 11 as before.

If a torque above a critical magnitude is then introduced into the shaft31 in the clockwise direction, although the forces which are producedare introduced into the tube 14 from the shaft 31 via the balls 4 asbefore, the magnitude of the forces which occur in the contact of theconvex shaped-out moldings 26 of the segments 15 with the shapedrecesses 28 of the tube 14 is so great that the tube 14 yieldselastically outward under this force. In the further course,accordingly, a relative rotation (even if it is small) of the shaft 31with respect to the tube 14 takes place in the clockwise direction. As aconsequence of this relative rotation, the play S in the return channels11 of the second circulatory channels 6 is reduced, in the second andfourth quadrants. At the same time, a play is produced for the balls 4in the loadbearing channels 10 of the second circulatory channel 6. InFIG. 1, these are the balls 4 in the loadbearing channels 10 in thesecond and fourth quadrants. Finally, the play S is canceled in thereturn channel 11 of the second circulatory channel 6, and the balls 4are clamped under load between the ball grooves 34 of the shaft 31 onone side and the ball grooves 23 of the segments 16 on the other side.In this situation, the torque is accordingly transmitted by the balls 4of all the circulatory channels 5, 6. Accordingly, above the criticaltorque, the arrangement of the return channel 8, 11 and of theloadbearing channel 7, 10 is reversed in the second circulatory channel6 which has been connected. This reversal occurs during rotation of thetwo profile elements 1, 2 with respect to one another, a play originallyformed in the return channels 8, 11 being canceled and, in contrast, aplay being produced in the loadbearing channels 7, 10.

It goes without saying that, in a corresponding way, torques above acritical magnitude can be introduced into the shaft 31 in thecounterclockwise direction, a corresponding reversal of the loadbearingchannels and return channels of the circulatory channels which areconnected taking place.

LIST OF REFERENCE NUMERALS

-   1 Outer profile element-   2 Inner profile element-   3 Rolling body-   4 Balls-   5 First circulatory channel-   6 Second circulatory channel-   7 Loadbearing channel-   8 Return channel-   9 Deflection channel-   10 Loadbearing channel-   11 Return channel-   12 Deflection channel-   13 Hollow body-   14 Tube-   15 Segment-   16 Segment-   17 Raceway-   18 Raceway-   19 Ball groove-   20 Ball groove-   21 Raceway-   22 Raceway-   23 Ball groove-   24 Ball groove-   25 Cap-   26 Shaped-out molding-   27 Shaped-out molding-   28 Shaped recess-   29 Deflection track-   30 Deflection track-   31 Shaft-   32 Tooth-   33 Ball groove-   34 Ball groove-   35 Cylindrical circumferential section

1. A linear rolling bearing for transmitting torques about itslongitudinal axis, having an inner profile element (2) and an outerprofile element (1) which surrounds the inner profile element (2) atleast partially, the two profile elements (1, 2) being mounted viarolling bodies (3) such that they can be displaced with respect to oneanother in the longitudinal direction, which rolling bodies (3)circulate endlessly in at least one first circulatory channel (5) and inat least one second circulatory channel (6), the circulatory channel (5,6) having a loadbearing channel (7, 10) which is parallel to thelongitudinal axis, a return channel (8, 11) which is parallel to thelongitudinal axis, and two deflection channels (9, 12) which connect theloadbearing channel (7, 10) and the return channel (8, 11) to oneanother in an endless manner, the rolling bodies (3) which are arrangedin the loadbearing channel (7) of the first circulatory channel (5)being provided for transmitting a torque between the two profileelements (1, 2), and the rolling bodies (3) which are arranged in theloadbearing channel (10) of the second circulatory channel (6) beingprovided to transmit a torque in the opposite direction between the twoprofile elements (1, 2), characterized in that the first circulatorychannel (5) and the second circulatory channel (6) can be connected toone another for jointly transmitting torques, the return channel (8, 11)of the circulatory channel (5, 6) which can be respectively connectedbeing used as a loadbearing channel and the loadbearing channel (7, 10)of the circulatory channel (5, 6) which can be respectively connectedbeing used as a return channel.
 2. The linear rolling bearing as claimedin the features of the precharacterizing clause of claim 1, in whichsubstantially only the loadbearing channel (7, 10) of the first orsecond circulatory channel (5, 6) is provided below a critical torquefor transmitting the torque, the return channel (8, 11) of therespective other circulatory channel (5, 6) being provided additionallyabove the critical torque as a loadbearing channel for transmitting thistorque, and the loadbearing channel (7, 10) of said other circulatorychannel (5, 6) being provided as a return channel.
 3. The linear rollingbearing as claimed in claim 1 in which a rotational angle of the twoprofile elements (1, 2) with respect to one another about thelongitudinal axis is a function of the prevailing torque, a criticalrotational angle being exceeded above the critical torque, at whichcritical rotational angle the return channel (8, 11) is used as aloadbearing channel and the loadbearing channel (7, 10) is used as areturn channel in the circulatory channel (5, 6) which is connected. 4.The linear rolling bearing as claimed in claim 1, in which theloadbearing channel (7, 10) and the return channel (8, 11) are delimitedin each case by an outer raceway (17, 18, 21, 22) for the rolling bodies(3), which outer raceway (17, 18, 21, 22) is assigned to the outerprofile element (1), and by an inner raceway (33, 34) for the rollingbodies (3), which inner raceway (33, 34) is assigned to the innerprofile element (2).
 5. The linear rolling bearing as claimed in claim1, in which the deflection channel (9, 12) is delimited by an outerdeflection track (29, 30) which is assigned to the outer profile element(1) and by an inner deflection track (35) which is assigned to the innerprofile element (2).
 6. The linear rolling bearing as claimed in claim4, in which the rolling bodies (3) are arranged in the return channel(8, 11) with play S with respect to the raceways (17, 21, 33, 34) whichdelimit the return channel (8, 11).
 7. The linear rolling bearing asclaimed in claim 4, in which the rolling bodies (3) are arranged withoutplay in the loadbearing channel (7, 10), in roller contact with theraceways (18, 22, 33, 34) which delimit the loadbearing channel (7, 10).8. The linear rolling bearing as claimed in claim 6, in which the playof the rolling bodies in the return channel (8, 11) of the circulatorychannel (5, 6) which can be connected is reduced during a rotation ofthe two profile elements (1, 2) with respect to one another.
 9. Thelinear rolling bearing as claimed in claim 7, in which the play of therolling bodies (3), with respect to the raceways (33, 34, 18, 22), inthe loadbearing channel (7, 10) of the circulatory channel (5, 6) whichcan be connected increases during a rotation of the two profile elements(1, 2) with respect to one another.
 10. The linear rolling bearing asclaimed in claim 1, in which the outer profile element (1) has a hollowbody (13) and the inner profile element (2) has a shaft (31), aplurality of segments (15, 16) which are distributed over thecircumference and delimit the circulatory channels (4, 5) together withthe shaft (31) being provided between the hollow body (13) and the shaft(31).
 11. The linear rolling bearing as claimed in claim 10, in -whichevery segment (15, 16) is provided with the two outer raceways (17, 18)which are arranged parallel to one another, and with two deflectiontracks (29, 30) which connect said raceways (17, 18) to one another. 12.The linear rolling bearing as claimed in claim 10, in which the segment(15, 16) is supported on the hollow body (13) in order to transmit atorque.
 13. The linear rolling bearing as claimed in claim 11, in whichthe outer raceway (17, 18) is configured as a ball groove (19, 20, 23,24) on that side of the segment (15, 16) which faces the shaft (31), aconvex shaped-out molding (26, 27) of the segment (15, 16) being formedon its side which faces the hollow body (13).
 14. The linear rollingbearing as claimed in claim 13, in which the shaped-out molding (26, 27)of the segment (15, 16) bears against a rest of the hollow body (13) inorder to transmit a torque.
 15. The linear rolling bearing as claimed inclaim 14, in which the hollow body (13) is provided with a plurality ofshaped recesses (28) which are distributed over the circumference,project radially inwardly and form rests for the segments (15, 16) inorder to transmit a torque.
 16. The linear rolling bearing as claimed inclaim 10, in which the shaft (31) has a plurality of teeth (32) whichare distributed over the circumference, are arranged parallel to thelongitudinal axis and on which the raceways (33, 34) are formed.
 17. Thelinear rolling bearing as claimed in claim 16, in which teeth (32) whichare adjacent to one another delimit in each case a convexly curvedcircumferential section (35) of the shaft (31) between them.
 18. Thelinear rolling bearing as claimed in claim 17, in which thecircumferential section (35) delimits the deflection channel (5, 6), asdeflection track for the rolling bodies (3).
 19. The linear rollingbearing as claimed in claim 10, in which the hollow body (13) can bedeformed resiliently.